Drive and support system for vibratory parts feeder

ABSTRACT

There is provided an improved spring system for a vibratory parts feeder bowl which is characterized by two separate spring systems, one of which functions primarily to guide the bowl along a predetermined, inclined, arcuate path (which may be a closed loop), and the other of which functions to store and release energy imparted to the bowl by a vibration inducing device at an energy level greater than can be sustained by a conventional spring system.

United States Patent [72] Inventor [56] References Cited UNITED STATES PATENTS 4/1958 Morris.......................... 2,922,514 1/1960 Carrier..... 2,985,279

Warren C. Burgess, Jr. Avon Lake, Ohio 868,128

[21] Appl. No. [22] Filed X 0 0 0 2 2 2 222 2 2888 /9 9 9 8 l l 1 9 l Oct. 21, 1969 [45] Patented Oct. 19, 1971 [73] Assignee Burgess & Associates, Inc.

Lakewood, Ohio AttorneyMcNenny, F arrington, Pearne & Gordon [54] DRIVE AND SUPPORT SYSTEM FOR VIBRATORY ABSTRACT: There is provided an improved spring system for PARTS FEEDER a vibratory parts feeder bowl which is characterized by two separate spring systems, one of which functions primarily to guide the bowl along a predetermined, inclined, arcuate path 10 Claims, 3 Drawing Figs.

(which may be a closed loop), and the other of which functions to store and release energy imparted to the bowl by a vibration inducing device at an energy level greater than can be sustained by a conventional spring system 220 BC, 220 BB; 271/89 PATENTEDnm 19 IQTI 3. 6 1 3 .870

, SHEET 2 BF 2 IN v E N T0 R WARREN C. BURGESS, JR.

A TTORN Y3 DRIVE AND SUPPORT SYSTEM FOR VIBRATORY PARTS FEEDER BACKGROUND OF INVENTION AND PRIOR ART This invention relates, as indicated, to vibratory conveying apparatus, and more particularly to vibratory apparatus of the bowl type which is particularly useful as a parts feeding device in automated systems. In such systems, parts may be vibratorily isolated and conveyed from a random supply thereof contained in a bowl along a trackway supported on the sidewall of the bowl and generally spiraling from the bottom thereof to an upper amrginal edge of the bowl. Along the trackway, there may be provided tooling for selecting from those parts moving along the trackway under vibratory impulses those which are properly oriented and rejecting disoriented parts for return to the random supply contained within the bowl. Properly oriented parts are discharged from the upper marginal edge of the bowl through a suitable escape mechanism for use in further assembly with other parts or for the performance of certain operations thereon, e.g., centerless grinding.

An advance in the art was made at the time bowls were first supported on glass fiber-reinforced resinous flat springs. Such resinous springs were able to withstand flexure over a much longer period of time than the steel springs, and were able to store and release energy at a higher level than steel springs.

A still further advance in the art was made when the means by which such bowls were driven in an oscillatory manner were changed from electrical and mechanical drive means to pneumatic drive means. Pneumatic drive means, especially those utilizing a free piston oscillating within a cylinder, enabled the application of much higher frequencies and amplitudes of vibration than theretofore possible with, for example, electromagnetic or mechanical vibratory driving means. The performance of glass fiber-reinforced resinous springs in combination with pneumatic vibration inducing means enabled the achievement of frequencies and amplitudes of vibration which could not be withstood by steel springs.

A still further advance in the art was made when it was discovered that with pneumatic free piston vibration inducing devices a measure of control over frequency, independently of amplitude of vibration, was possible by controlling the pressure of the gas introduced into the vibration inducing device, and by controlling the pressure drop of the gas through the apparatus. By controlling the inlet pressure of the fluid to the pneumatic vibration inducing device, one was able to control frequency of vibration. Still further, by controlling the pressure drop of fluid through the apparatus, one was able to control substantially independently of frequency the amplitude of vibration.

These developments enabled a great expansio n in the nature of the materials which could be handled by vibratory means and enabled delivery of parts at rates previously unattainable.

It has now been found that the rate of supply of parts can be further extended beyond the ability of glass fiber-reinforced resinous springs alone to withstand the power inputs demanded by such increased rates of feeding.

Reference may be had to my prior U.S. Pat. No. 2,861,548 for the details of a pneumatic free piston vibration inducing device useful in accordance with the present invention, the disclosure of which is incorporated herein by reference.

Reference may also be made to my US. Pat. No. 3,023,738 for details of construction of a power control system for a pneumatic free piston vibration inducing device, and particularly a parts feeding bowl, the disclosure of which is incor porated herein by reference.

Reference may also be made to my US. Pat. No. 3 ,280,964for details of a vibratory parts feeder bowl construction which may be utilized in accordance with the present invention, the disclosure of which is incorporated herein by reference.

As indicated above, the power requirements under certain conditions are such that flat steel springs cannot possibly withstand high energy input levels without failure, and even glass fiber-reinforced resinous springs cannot long withstand such energy requirements. While such glass fiber-reinforced resinous springs may withstand much higher energy levels than steel springs, nevertheless they do have a limit. In order to achieve higher frequencies of vibration for more rapid feed rates of parts, for example, the thickness of the flat spring must be increased. With glass fiber-reinforced resinous springs, the stress within the spring increases as the cube of the thickness. Consequently, where the amplitude of vibration must also be relitively high, such thick springs undergo an end failure which is unique to resinous springs.

Coil springs, on the other hand, are capable of storing and releasing large quantities of energy, but it is difficult to control their path of movement as they are not sufficiently resistant to extraneous forces, e.g., change of position or magnitude of the load of parts carried in the bowl. In the high-speed transmission of parts and their orientation during transmission, uniformity in the path and the nature of vibration is essential.

It has now been found that satisfactory high energy vibratory transmission of parts can be successfully achieved by utilizing a pair of spring systems, one of which is a leaf type spring system, and the other of which is an auxiliary spring system which may be of either the leaf type or the coil spring type. Best results have been obtained where the system for guiding the bowl along a predetermined, inclined, arcuate path comprises flat springs, preferably of the glass fiber-reinforced resinous type, and the auxiliary spring system for storing and releasing energy is composed of steel coil springs.

BRIEF STATEMENT OF THE INVENTION Briefly stated, therefore, the present invention is in the provision of a drive and support system for a vibratory parts feeding bowl which comprises in combination a base, a plate adapted to support a walled structure to define a bowllike receptacle for parts, and a pair of spring systems. The first spring system includes a plurality of inclined flat springs radially disposed about an axis normal to and extending through the center of the plate. Each of the springs is secured at one extremity to the base and at the other extremity to the plate for guiding the plate along a predetermined oscillatory path. A second or auxiliary spring system includes a plurality of springs radially disposed about the same axis and on a different diameter from that of the flat springs and coacting between the base and the plate for storing and releasing energy imparted to the plate. There is also provided vibratory drive means for oscillating the plate along said predetermined path.

In the preferred embodiment, therefore, the present invention comprises a parts feeding bowl supported relative to a base, preferably a massive base, upon a plurality of inclined leaf type springs radially disposed about a central axis. These springs are generally designed for no more than guiding the bowl through a predetermined, inclined, arcuate path. Alone, the leaf spring system would be found inadequate to deliver parts at the demand rate. It should be noted at this point that the inclined arcuate path is seldom linear and is more frequently an orbital path due to slight movement of the base. If the base were of infinite mass, then the path followed by any point on the surface of the bowl would be inclined, arcuate and linear. However, since the base must be a finite mass, it moves slightly, and accordingly the path followed by a point on the surface of the bowl supported thereon will tend to be orbital or a closed loop as distinct from linear.

In concentric relation to the leaf type springs, there is a secondary or auxiliary set of springs, preferably coil springs, which are disposed for coaction between the bowl and the base in such a way as to store and release energy applied to the bowl by a vibration inducing device. The characterizing feature of the present invention, therefore, is a pair of spring systems preferably in concentric relation to each other, one of which is designed primarily for guiding the bowl along a predetermined path, and the other of which is designed primarily for the storage and release of energy imparted to the bowl. Each of the spring systems comprises a plurality of spring stations at circumferentially spaced intervals about a common axis.

For general operation, the spring systems are at uniformly spaced intervals about the common axis. There may be in special applications where the vibrating amss is asymmetric a need for either balancing the vibrating mass or achieving effective balance by nonuniform spacing of the external springs, or possibly by using springs of different spring constants and characteristics at different points on the circumference. Thus, complete uniformity is the starting point. In practice it may be found convenient to deviate from this in accordance with the need for an asymmetric spring system. For best results, the number of spring stations in each system is an even number and of like number to the other spring system.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a top view of an embodiment of my invention showing a portion of a massive base and a plate supported in spaced relation to the base by a pair of concentrically disposed spring systems.

FIG. 2 is a view of a pair of spring stations showing in dotted lines a flat spring and its mounting for the flat spring guiding system, and opposed coil springs constituting an auxiliary spring station for storage and release of energy as they appear in the plane indicated by the line 22 in FIG. 1.

FIG. 3 is a diagram illustrating a method for graphically determining the angle of disposition of the coil spring axes.

DETAILED DESCRIPTION OF THE DRAWINGS Referring now more particularly to FIGS. 1 and 2, there is here partially shown a drive and support system including a massive base having a mass greater than the total mass of the equipment and parts being handled supported thereon. In spaced relation to the base 10, there is provided a plate 12. The plate 12 is adapted to carry a bowl-type vibratory receptacle, such as a bowl-type receptacle shown and described in my aforesaid U.S. Pat. No. 3,280,964, the disclosure of which is incorporated herein by reference thereto. It should be understood, however, that any type of vibratory bowl-type receptacle may be used with the present invention. Such bowls are normally characterized by a recessed central portion which acts as a supply receptacle for a plurality of randomly disposed parts, e.g., nails, bolts, washers, transistors, bottle caps, etc. The bowl is characterized by upstanding walls wyich support a spiral trackway leading, generally, upwardly and outwardly from the bottom of the bowl to the upper marginal edge. The trackway may be designed to accommodate parts only in a certain predetermined spatial arrangement, or to include along the trackway various devices and mechanisms for ejecting parts which are improperly oriented. The design of the bowl, the trackway, and the tooling along the trackway fonns no part of the present invention. The plate 12 may be integral with the bowl, or it may provide a platform to which a bowl is secured, as by bolts.

The plate 12 is supported in spaced relation to the base 10 by two separate spring systems. The first of these spring systems is composed of a plurality, e.g., four in number, of leaf type or flat spring stations 14, 16, 18, and radially disposed about a central axis 22a extending through the center of and normal to the plate 12. The flat spring stations l4, l6, l8, and 20 are all identical in structure and circumferentially disposed at 90 intervals about the axis 22a. As best shown in FIG. 2, flat spring station 20 is composed of a flat or leaf type spring 22 which may, for convenience, have a configuration such as that fully shown and described in my prior U.S. Pat. No. 2,985,280 dated May 23, 1961. Alternatively, the flat springs may be rectangular in configuration. The springs forming a part of the spring stations 14, 16, 18, and 20 may be formed of spring steel, or they may be formed of laminations of plies of glass fiber-reinforced resinous material such as an epoxy resin.

Such springs are conventional and readily obtainable in the trade. The glass fiber-reinforced resinous springs are preferred.

The means for securing the springs such as flat spring 22 to the massive base 10 conveniently include a sping block 24 having a sloping face 26 against which one of the faces of the spring 22 is clamped The slope is predetermined and is conveniently about 60 to the horizontal or top surface of the base 10. In general, the slope of the flat springs may range from about 45 to relative to the horizontal. The clamping means include the clampling bar 28 and bolts, e.g., a bolt 30 fitted with a washer 32 and threadedly engaged in the spring block 24. Usually two bolts 30 in side-by-side relation are utilized to secure one end of the spring 22 to the base 10. The spring block 24 may be secured to the base 10 by any suitable means such as welding or bolting. In like manner, a complementarily shaped spring mounting block 34 is secured by any suitable means to the underside of plate 12, and the upper end of the spring 22 secured against the sloping face 36 by means of a clamping bar 38, the bolt 40, and a lock washer 42 in a manner similar to the mode of securement of the spring to the base. The angle of the spring with respect to the vertical is conveniently about 30, although this may vary substantially.

It should be noted that the springs constituting the flat spring system of the present invention are designed not for the purpose of storing and releasing energy, but merely for the purpose of guiding the plate 12 as it oscillates along an inclined arcuate path having both vertical and horizontal components in response to vibrations induced therein as hereinafter described. Accordingly, instead of fixed mountings as above described, the springs may have their ends disposed in pockets or slots in the base 10 and the plate 12, respectively, with attachment being effected by gravity. These springs have a thickness which is generally less than that which would be required to sustain a proper frequency of vibration, and also a desired amplitude of vibration. Thus, the flat springs are improperly designed for the storage and release of energy of the magnitude required, but are adequately designed for the functions of supporting the bowl and contents and guiding the plate 12 along the predetennined path.

In an exemplary embodiment, the flat springs were glass fiber-reinforced resinous 25 ply (0.0l0-inch thick plies) X 6" X2 with an active spring dimension of 3.625 inches. Springs of this size are selected because the stress levels encountered at the amplitudes at which the present devices may be run are well below those which will fail such springs.

In the exemplary embodiment illustrated in FIGS. 1 and 2, a vibration inducing device is shown in dotted lines, and is generally indicated by the number 44. This device includes a flange 46 for abutting relation to the underside of the plate 12 and securing thereto by means of bolts 47. The construction of the vibration inducing device is relatively unimportant to the present invention, although a pneumatic vibration inducing device of the type which is shown in my U.S. Pat. No. 2,985,280 is quite satisfactory for the purposes of the present invention. In view of the fact that very high energy levels productive of high frequency of vibration and/or large amplitude of vibration and high rate of delivery is desired in devices of the present structure, the diameter of the piston is quite substantial as shown in FIG. 1, and the length of the piston is relatively short to allow for high frequency of oscillation. In the aforesaid exemplary embodiment, the piston weighed 10.25 pounds and oscillated along a l-inch total stroke at a frequency of 2,800 cycles per minute with air pressure of 60 p.s.i.g. The energy level of such a piston is beyond the ability of any known flat spring system to contain it for production purposes. Such a piston imparted to a bowl a frequency of 2,800 cycles per minute at an amplitude of 0.255 inches measured on a radius of 15 inches from the bowl center.

The mode of operation of the piston is as shown and described in my aforesaid U.S. Pat. No. 2,985,280. It should be understood, however, that any suitable vibration inducing unrnnL n-mn device may be used in the present invention, and accordingly, electromagnetic vibration drive means and mechanical vibration drive means are contemplated for use in this invention. Best results are assured, however, with a pneumatic vibration inducing device.

As shown in FIG. 2, the vibration inducing device 44 is axially mounted and the axis of the piston within the cylinder along which the piston oscillates coincides with the vertical axis 22a of the plate 12. This is a convenient mode of attachment of the vibratory drive means to the apparatus. Alternatively, the piston may be caused to oscillate along a horizontal axis or on a line normal to the angle of the leaf springs or any intermediate angular positions. A general mode of accomplishing this type of lateral mounting of vibratory drive means is disclosed in my prior U.S. Pat. No. 3,367,480 dated Feb. 6, 1968, the disclosure of which is incorporated herein by reference.

When the vibration inducing device is mounted as shown in FIG. 1, one obtains optimum and uniform quality of feeding action around the bowl. A lateral or side arm mounting yields optimum load carrying ability at some sacrifice in quality of feeding action even when the bowl is closely balanced. The mode of mounting is optional.

The maximum energy level of a system is any combination of frequency of vibration and movement (e.g., amplitude) which stresses an ideal or near ideal flat spring system to the point where the system will no longer last in continuous production. For example, an energy level expressed as polar inertia (1,,g) in pound-inches in excess of 6,800 pound-inches at 2,6002,800 cycles per minute and an amplitude of 0.250 inches cannot be sustained by known flat spring systems. For reasons of geometry and strength of materials, it is not presently possible to build a flat spring system which will withstand such energy levels. With the dual spring systems of the present invention, such limiting energy levels are readily exceeded.

In order to absorb and release the large amounts of energy imparted to the plate 12 by the vibration inducing device 44, there are provided a plurality of coil spring stations generally indicated at 48, 50, 52, and 54. The coil spring stations are disposed preferably in concentric relation to the flat spring stations, preferably on a radius which is larger than the radius of the flat spring stations. Such spring stations may be disposed on the same radius as the flat spring centerlines alternately with the flat spring stations. It is more convenient for design reasons that they be located on different radii. In the same manner as the components of the flat spring system, the components of the coil spring, energy storage and release systems are disposed at 90 intervals. Although these are shown to be at the same intervals as the flat spring components, the coil springs may be disposed at uniform angular dispositions intermediate the angular dispositions of the flat spring stations. As indicated above with respect to the disposition of the flat springs, the coil spring stations may also be asymmetrically disposed to account for asymmetric inertial forces created by a specific bowl.

As best shown in FIG. 2, the individual coil spring stations are each composed of a spring support member 56 having a pair of laterally extending flanges 58 and 60 suitably bored to receive a mounting bolt 62 and 64, respectively, for threaded engagement with and attachment to the base and locked into position by means of lock washers 66 and 68, respectively. The upper face 70 of the support member 56 is desirably, although not essentially, beveled to provide a surface which lies in a plane which closely approximates and parallels the path followed by a point on the plate 12 as it oscillates in response to the vibratory impulses imparted by the drive means 44. The upper face 70 may be horizontally disposed, although optimum results are obtained with the sloped support. The upper face 70 is elongated and rectangular, and is conveniently provided with upstanding abutment support brackets 72 and 74 at opposite ends thereof. Upstanding bracket 72, which is conveniently welded to the support member 56, is bored and tapped to receive and retain in threaded engagement therewith a bolt 76 fitted with a spring abutment plate 78 adjacent its distal extremity 80. The spring abutment plate 78 may be welded to the bolt 76. Thus, the spatial disposition of the abutment plate 78 along an inclined path paralle to the surface 70 may be adjusted, and its position secured by means of a lock nut 82 coacting between the bolt 76 and the upstanding abutment bracket 72.

In like manner adjacent the opposite end of the upper face 70, the upstanding spring abutment bracket 74 is likewise bored and tapped for threaded engagement with a bolt 84 fitted adjacent its distal extremity 86 with an abutment member 88, and held at a preselected position by means of a lock nut 90 coacting between the bolt 84 and the abutment bracket 74. The abutment member 88 may be rotatable relative to the bolt 84, and to secure the abutment 88 to the end of the bolt 84, there may be utilized a pin 92, and a centering boss 94 coacting with either side of the abutment plate 88 and confining the plate therebetween. Adjustability of the coil spring abutments while desirable is not essential.

The bolts 76 and 84 lie on a common axis which is conveniently parallel to the upper face 70 of the support 56.

Turning now to the structure of the plate 12, there are provided four radially extending lugs 96, 98, 100, and 102 at 90 intervals directly opposite the location of the spring stations 14, l6, l8, and 20. The lugs 96, 98, 100, and 102 are conventiently welded to the plate 12, although any suitable means of securing may be employed. The lugs 96, 98, 100, and 102 support spring blocks 104, 106, 108, and 110, respectively, which are disposed so as to have parallel faces, e.g., faces 112 and 114 lying in planes for disposition normal to the axis of bolts 76 and 84, respectively. The faces 112 and 114 provide, therefore, spring abutment surfaces for the coil springs. Each of the spring blocks 104, 106, 108, and is conveniently provided with a centrally disposed pin, e.g., pin 116, which extends bilaterally from each of the faces 112 and 114 and provides a convenient retaining means for the coil springs. To complete the coil spring station, there are provided coil springs I18 and 120, preferably of spring size and properties as dicated by the needs. These are standard flat ground coil springs readily obtainable on the market. The coil springs can range from identical springs to quite dissimilar springs in size and properties. The coil springs are centered on the extensions of pin 116 from surfaces 112 and 114, respectively, and also upon the extremities 80 and 86 of the bolts 76 and 84, respectively. The bolts, the springs, and the pin 116 all lie, therefore, on a common inclined axis. In the exemplary embodiment, four coil springs l-inch diameter by 2 inches long having a spring constant of l87 pounds per Aa-inch deflection, and four coil springs 1.5-inch diameter by 2.5 inches long having a spring constant at 275 pounds per 41-inch deflection were used in the manner shown in the drawings. Their axes were disposed at an angle of 20 to the horizontal.

The angle of inclination of the aforesaid axis is, it will be observed, not normal to the surface of the spring 22 at zero displacement. This is occasioned by the fact that the lateral projections extending from the plate 12 are more remote from the central axis 22a than the centerlines of the inclined flat springs, e.g., spring 22. With increasing distance from the axis, the inclination of the aforesaid coil spring axis becomes increasingly displaced from a position in a plane perpendicular to the plane of the flat springs.

A mode of determining the angle of inclination of the axis is graphically illustrated in FIG. 3. Beginning at the point 0, which represents the center of the bowl or the plate 12, as the case may be, there is located on the horizontal line a point A a distance from 0 equal to the radious at the centerline of spring 22. A vertical line is erected at point A. With 0 as the origin, an angle 0 is erected equal to the angle by which the flat spring 22 deviates from the vertical. The intersection of this line with the vertical erected at A determines the point B. A second vertical line is erected at point C which represents a convenient radius on which the centerline of the axiliary spring stations is located. A horizontal line parallel to the line AC is drawn through B to its interscetion D with the second vertical line erected at point C. The line OD is drawn defining the angle 0. The angle is the slope of the face 70 and the axis of the coil springs 118 and 120. ln the embodiment shown, the slope of the face 70 is about 20.

As indicated above, disposition of the axes of the coil springs on an angle determined in the manner above described yields the best results in terms of performance. However, the structure may be simplified by disposing the axes of the coil springs on a horizontal line or upon an angle other than as calculated above. The performance is less than optimum in such cases.

As is shown best in FIG. 1, where different sized coil springs are used, for example, as illustrated by coil springs 118 and 120, pairs of similarly sized springs are used for the other coil spring stations 48, 50, and 52, but the position of the coil springs is reversed alternately at successive stations in asymmetric distribution. Thus, whereas the heavier coil spring is in the uppermost position at coil spring station 54, the heavier coil spring 128 is in a lower position in coil spring station 48. Then in coil spring station 50, the heavier spring is again in the uppermost position as shown at l20b. ln mounting the coil springs 118 and 120, for example, they are each desirably, although not essentially, placed under slight compression at zero displacement of the plate 12. In like manner, the coil springs at stations 48, 50, and 52 are also maintained under slight compression at zero displacement.

As above indicated, the coil spring stations 48, 50, 52, and 54 have the primary purpose of storing and releasing energy imparted to the plate 12. Thus, large quantities of energy may be imparted to give, for example, large amplitudes of vibration at high frequency. This enables the movement of parts from a bowl mounted on the plate 12 at a high rate ofspeed as may be demanded by machinery carrying out further operations on the part or assembling the parts into subassemblies. The energy levels at which the devices of the present invention are capable of operating far exceed the capacities of flat springs to hold up for any appreciable period of time. To obtain high frequencies of vibration, and high amplitudes of vibration, the thickness of the resinous springs or steel springs has to be so great that early stress failure is experienced. However, with the very much thinner leaf type or flat springs serving primarily for supporting and guiding the apparatus along a predetermined path, and utilization of a coil spring system enables the inposition of energy levels upon the device which permit the achievement of energy levels sufficient to secure rates of feed not heretofore obtainable. Productivity is proportional to the energy level.

What is claimed is:

l. A drive and support system for a vibratory parts feeding bowl comprising in combination:

a. a base;

b. a plate adapted to support a walled structure to define a bowllike receptacle for parts;

c. a first spring system including a plruality of inclined flat springs radially disposed about an axis normal to and extending through the center of said plate, each of said springs being anchored at one extremity to said base and at the other to said plate at a predetermined angle of inclination for supporting and guiding said plate along a predetermined oscillatory path;

d. a second spring system including a plruality of auxiliary spring stations radially disposed about the same axis as said flat springs, and coacting between said base and said plate for storing and releasing energy imparted to said plate, each spring station of said second spring system including:

1. a stationary support mounted on the base;

2. a pair of spaced spring abutments;

3. a pair of axially aligned pins extending toward each other from said abutments, respectively, the axis of said pins being inclined relative to said plate; and 4. a pair of C01] springs fitted over said pins, respectively;

and in which system the plate includes:

5. a radially extending lug block adapted to be disposed between said pair of coil springs at each said spring station; and

6. a pair of axially aligned pins extending laterailly from said lug block for insertion in the confronting ends of said coil springs; and

e. vibratory drive means for imparting energy to said plate for oscillating said plate along said predetermined path.

2. A system in accordance with claim 1 in which the flat springs are glass fiber-reinforced resin springs.

3. A system in accordance with claim 1 in which the flat springs are spring steel springs.

4. A system in accordinace with claim 1 in which the plate is integral with the walled structure.

5. A system in accordance with claim 1 in which the plate is separate from the walled structure.

6. A system in accordance with claim 1 in which the second spring system comprises a plurality of auxiliary spring stations each including stationary spring support means mounted on the base and having a spring abutment portion, each auxiliary spring in said auxiliary station coacting between said plate and said abutment portion.

7. A system in accordance with claim 1 in which the spring abutment portions are adjustable.

8. A system in accordance with claim 1 in which the second spring system includes four spring stations.

9. A system in accordance with claim 1 in which the coil springs of each pair have a different diameter.

10. A system in accordance with claim 1 in which the drive means is a pneumatic free piston vibration inducing device. 

1. A drive and support system for a vibratory parts feeding bowl comprising in combination: a. a base; b. a plate adapted to support a walled structure to define a bowllike receptacle for parts; c. a first spring system including a plruality of inclined flat springs radially disposed about an axis normal to and extending through the center of said plate, each of said springs being anchored at one extremity to said base and at the other to said plate at a predetermined angle of inclination for supporting and guiding said plate along a predetermined oscillatory path; d. a second spring system including a plruality of auxiliary spring stations radially disposed about the same axis as said flat springs, and coacting between said base and said plate for storing and releasing energy imparted to said plate, each spring station of said second spring system including:
 1. a stationary support mounted on the base;
 2. a pair of spaced spring abutments;
 3. a pair of axially aligned pins extending toward each other from said abutments, respectively, the axis of said pins being inclined relative to said plate; and
 4. a pair of coil springs fitted over said pins, respectively; and in which system the plate includes:
 5. a radially extending lug block adapted to be disposed between said pair of coil springs at each said spring station; and
 6. a pair of axially aligned pins extending laterailly from said lug block for insertion in the confronting ends of said coil springs; and e. vibratory drive means for imparting energy to said plate for oscillating said plate along said predetermined path.
 2. a pair of spaced spring abutments;
 2. A system in accordance with claim 1 in which the flat springs are glass fiber-reinforced resin springs.
 3. A system in accordance with claim 1 in which the flat springs are spring steel springs.
 3. a pair of axially aligned pins extending toward each other from said abutments, respectively, the axis of said pins being inclined relative to said plate; and
 4. a pair of coil springs fitted over said pins, respectively; and in which system the plate includes:
 4. A system in accordinace with claim 1 in which the plate is integral with the walled structure.
 5. A system in accordance with claim 1 in which the plate is separate from the walled structure.
 5. a radially extending lug block adapted to be disposed between said pair of coil springs at each said spring station; and
 6. a pair of axially aligned pins extending laterailly from said lug block for insertion in the confronting ends of said coil springs; and e. vibratory drive means for imparting energy to said plate for oscillating said plate along said predetermined path.
 6. A system in accordance with claim 1 in which the second spring system comprises a plurality of auxiliary spring stations each includinG stationary spring support means mounted on the base and having a spring abutment portion, each auxiliary spring in said auxiliary station coacting between said plate and said abutment portion.
 7. A system in accordance with claim 1 in which the spring abutment portions are adjustable.
 8. A system in accordance with claim 1 in which the second spring system includes four spring stations.
 9. A system in accordance with claim 1 in which the coil springs of each pair have a different diameter.
 10. A system in accordance with claim 1 in which the drive means is a pneumatic free piston vibration inducing device. 